CN111059241A

CN111059241A - Control device for vehicle power transmission device

Info

Publication number: CN111059241A
Application number: CN201910978171.4A
Authority: CN
Inventors: 河井健辅; 绫部笃志; 服部邦雄; 大形勇介; 大板慎司
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2018-10-16
Filing date: 2019-10-15
Publication date: 2020-04-24
Also published as: US20200114914A1; DE102019215323A1; JP2020062944A

Abstract

The invention provides a control device for a vehicle power transmission device, which can switch a two-way clutch into a one-way mode even in a driven state in the vehicle power transmission device configured to be provided with a first power transmission path and a second power transmission path in parallel. When a request for switching the two-way clutch (TWC) to the one-way mode is satisfied while the two-way clutch (TWC) is in the locked mode and the two-way clutch (TWC) is in the driven state during forward travel, the engine torque (Te) of the engine (12) is increased, whereby the torque acting on the drive side can be transmitted to the two-way clutch (TWC), and the two-way clutch (TWC) can be switched to the one-way mode. Thus, since the rotation is not transmitted to the first clutch (C1), the high rotation of the first clutch (C1) can be suppressed.

Description

Control device for vehicle power transmission device

Technical Field

The present invention relates to control of a vehicle power transmission device configured to include a first power transmission path and a second power transmission path in parallel between an engine and drive wheels.

Background

A vehicle power transmission device is known which includes a first power transmission path including a first clutch and a dog clutch and a second power transmission path including a continuously variable transmission and a second clutch, which are arranged in parallel between an engine and a drive wheel. The power transmission device described in patent document 1 is the vehicle power transmission device.

Prior art documents

Patent document

Patent document 1: international publication No. 2013/176208

Disclosure of Invention

Problems to be solved by the invention

In the power transmission device described in patent document 1, a dog clutch is provided in the first power transmission path. Further, when the first clutch becomes the high rotation running state, the high rotation of the first clutch is suppressed by releasing the dog clutch. However, since the dog clutch of patent document 1 is configured to include a synchronizing mechanism and the like, the number of components increases, and the manufacturing cost increases.

In contrast, for the purpose of reducing cost, it is conceivable to employ a two-way clutch instead of the dog clutch, the two-way clutch being configured to be switchable between a mode (hereinafter, referred to as a one-way mode) of a one-way clutch that transmits power acting in the forward direction of the vehicle and cuts off power acting in the reverse direction of the vehicle, and a mode (hereinafter, referred to as a lock-up mode) that transmits power acting in the forward direction of the vehicle and the reverse direction of the vehicle. In this way, when the vehicle is in a traveling state in which the first clutch is in a high-rotation state, the two-way clutch is switched to the one-way mode functioning as the one-way clutch, so that the rotation transmission to the first clutch is interrupted by the two-way clutch, and the high-rotation state of the first clutch can be suppressed.

In the power transmission device configured as described above, when a request to switch the bidirectional clutch from the lockup mode to the one-way mode is satisfied during traveling in a driven state in which the vehicle travels by inertia of the vehicle, members constituting the bidirectional clutch come into contact with each other and receive a force therebetween, and there is a possibility that the bidirectional clutch is not switched to the one-way mode. Further, if the two-way clutch is maintained in the locked mode even when the vehicle speed is shifted up, the first clutch may be rotated at a high rotation by the rotation transmitted from the drive wheels via the two-way clutch.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a control device for a vehicle power transmission device configured to include a first power transmission path and a second power transmission path in parallel between an engine and a drive wheel, the first power transmission path being configured to include a first clutch and a two-way clutch, and the second power transmission path being configured to include a continuously variable transmission and a second clutch, wherein even when a request for switching the two-way clutch to the one-way mode is satisfied during forward travel in a driven state, high rotation of the first clutch can be suppressed by switching the two-way clutch to the one-way mode.

Means for solving the problems

The first aspect of the invention is directed to a control device for a vehicle power transmission device (a) including two power transmission paths, a first power transmission path and a second power transmission path, arranged in parallel between an engine and a drive wheel, the first power transmission path including a first clutch and a sub clutch, the second power transmission path including a continuously variable transmission and a second clutch, the first power transmission path being configured to enable power transmission by engaging the first clutch and releasing the second clutch, the second power transmission path being configured to enable power transmission by releasing the first clutch and engaging the second clutch, and (b) the control device for a vehicle power transmission device being characterized in that, the sub clutch is constituted by a two-way clutch that is switchable between at least two modes, a one-way mode in which power is transmitted in a driving state of a vehicle and power is switched off in a driven state of the vehicle, and a lock-up mode in which power is transmitted in the driving state and the driven state of the vehicle, and (c) the control device of the power transmission device for a vehicle includes a control unit that increases an engine torque of the engine when a request to switch the two-way clutch to the one-way mode is satisfied during forward travel in the driven state with the two-way clutch in the lock-up mode.

A second aspect of the present invention provides the control device of the vehicle power transmission device recited in the first aspect of the present invention, wherein the control unit increases the engine torque of the engine when a difference in rotation speeds between the front and rear rotating members constituting the bidirectional clutch is equal to or less than a predetermined determination threshold value.

A third aspect of the invention provides the control device of the vehicle power transmission device recited in the first or second aspect of the invention, wherein the control unit temporarily increases the torque in the vehicle forward direction transmitted from the engine to the two-way clutch by increasing the engine torque.

Effects of the invention

According to the control device for the vehicle power transmission device of the first aspect of the invention, when the request to switch the two-way clutch to the one-way mode is satisfied while the forward travel is being performed in the driven state with the two-way clutch in the locked mode, the engine torque of the engine is increased to transmit the torque acting on the driving side to the two-way clutch, and the two-way clutch is switched to the one-way mode. Therefore, since the two-way clutch is switched to the one-way mode and the rotation is not transmitted to the first clutch, the high rotation of the first clutch can be suppressed.

Further, according to the control device of the vehicle power transmission device of the second aspect of the invention, since the engine torque of the engine is increased when the difference in the rotational speeds of the front and rear rotating members is equal to or less than the determination threshold value, the shock and deterioration in fuel efficiency due to the increase in the engine torque of the engine are avoided even though the bidirectional clutch is switched to the one-way mode.

Further, according to the control device for the vehicle power transmission device of the third aspect of the invention, the engine torque is increased so that the torque in the vehicle forward direction transmitted from the engine temporarily increases, and therefore the two-way clutch can be switched to the one-way mode.

Drawings

Fig. 1 is a diagram for explaining a schematic configuration of a vehicle to which the present invention is applied, and is a diagram for explaining a control function and a main part of a control system for various controls in the vehicle.

Fig. 2 is a diagram schematically showing the structure of the bidirectional clutch of fig. 1, and is a cross-sectional view in which a portion in the circumferential direction when switching to the one-way mode is cut.

Fig. 3 is a diagram schematically showing the structure of the bidirectional clutch of fig. 1, and is a cross-sectional view in which a portion in the circumferential direction when switched to the lockup mode is cut off.

Fig. 4 is an engagement operation table showing an engagement state of each engagement device for each operation position selected by a shift lever as a shift switching device provided in the vehicle.

Fig. 5 is a flowchart illustrating a main part of the control operation of the electronic control device of fig. 1, that is, the control operation when the bidirectional clutch is switched to the one-way mode while the bidirectional clutch is traveling in the locked mode and in the driven state.

Fig. 6 is a time chart showing a control result based on the control operation of the electronic control device of fig. 1, specifically, a control result when the operation position is switched from the M1 position to the D position while the vehicle is in the driven state and the bidirectional clutch is traveling in the lock-up mode.

Detailed Description

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the following embodiments, the drawings are simplified or modified as appropriate, and the dimensional ratios, shapes, and the like of the respective portions are not necessarily drawn accurately.

Examples

Fig. 1 is a diagram for explaining a schematic configuration of a vehicle 10 to which the present invention is applied, and is a diagram for explaining a control function and a main part of a control system for various controls in the vehicle 10. In fig. 1, a vehicle 10 includes a vehicle power transmission device 16 (hereinafter, referred to as a power transmission device 16) that transmits power of an engine 12 functioning as a power source to drive wheels 14.

The power transmission device 16 includes an engine 12, a known torque converter 20 as a fluid transmission device coupled to the engine 12, an input shaft 22 coupled to the torque converter 20, a belt-type continuously variable transmission 24 coupled to the input shaft 22, a forward/reverse switching device 26 similarly coupled to the input shaft 22, a gear mechanism 28 coupled to the input shaft 22 via the forward/reverse switching device 26 and disposed in parallel with the continuously variable transmission 24, an output shaft 30 as a common output rotating member of the continuously variable transmission 24 and the gear mechanism 28, a counter shaft 32, a reduction gear device 34 composed of a pair of gears that are disposed on the output shaft 30 and the counter shaft 32 so as to be incapable of relative rotation, a gear 36 that is disposed on the counter shaft 32 so as to be incapable of relative rotation, a differential device 38 that is coupled to the gear 36 so as to be capable of transmitting power, and a differential device 38, And left and right axles 40 coupled to the differential device 38.

In the power transmission device 16 configured in this manner, power output from the engine 12 is transmitted to the left and right drive wheels 14 via the torque converter 20, the forward/reverse switching device 26, the gear mechanism 28, the reduction gear device 34, the differential device 38, the axle 40, and the like in this order. Alternatively, in the power transmission device 16, the power output from the engine 12 is transmitted to the left and right drive wheels 14 via the torque converter 20, the continuously variable transmission 24, the reduction gear device 34, the differential device 38, the axle 40, and the like in this order. Without special distinction, the power is also synonymous with torque or force.

As described above, the power transmission device 16 includes the gear mechanism 28 and the continuously variable transmission 24, which are provided in parallel on the power transmission path PT between the engine 12 and the drive wheels 14. Specifically, the power transmission device 16 includes two power transmission paths that are provided in parallel between the input shaft 22 and the output shaft 30 and that can transmit the power of the engine 12 from the input shaft 22 to the output shaft 30. The two power transmission paths are constituted by a first power transmission path PT1 via the gear mechanism 28 and a second power transmission path PT2 via the continuously variable transmission 24. In this way, the power transmission device 16 includes two power transmission paths, i.e., a first power transmission path PT1 and a second power transmission path PT2, in parallel between the input shaft 22 and the output shaft 30. The input shaft 22 is a common input shaft for the first power transmission path PT1 and the second power transmission path PT2, and the output shaft 30 is a common output shaft for the first power transmission path PT1 and the second power transmission path PT 2.

The first power transmission path PT1 is a power transmission path that includes the forward/reverse switching device 26 including the first clutch C1 and the first brake B1, the gear mechanism 28, and the two-way clutch TWC functioning as a sub-clutch, and transmits the power of the engine 12 from the input shaft 22 to the drive wheels 14 via the gear mechanism 28. In the first power transmission path PT1, the forward/reverse switching device 26, the gear mechanism 28, and the two-way clutch TWC are arranged in this order from the engine 12 toward the drive wheels 14. That is, the first clutch C1 is disposed on the engine 12 side of the two-way clutch TWC. The second power transmission path PT2 is a power transmission path that includes the continuously variable transmission 24 and the second clutch C2 and transmits the power of the engine 12 from the input shaft 22 to the drive wheels 14 via the continuously variable transmission 24. In the second power transmission path PT2, the continuously variable transmission 24 and the second clutch C2 are arranged in this order from the engine 12 toward the drive wheels 14.

The gear ratio EL (i.e., the input shaft rotation speed Nin/the output shaft rotation speed Nout) in the first power transmission path PT1 including the gear mechanism 28 is set to a value larger than the maximum gear ratio in the second power transmission path PT2, that is, the lowest-side gear ratio γ max of the continuously variable transmission 24. That is, the gear ratio EL is set to a gear ratio on the low speed side of the lowest gear ratio γ max. Thus, the second power transmission path PT2 has a speed change ratio on the higher speed side than the first power transmission path PT 1. The input shaft rotation speed Nin is the rotation speed of the input shaft 22, and the output shaft rotation speed Nout is the rotation speed of the output shaft 30.

The continuously variable transmission 24 includes a first shaft 58 provided coaxially with the input shaft 22 and integrally connected to the input shaft 22, a primary pulley 60 having a variable effective diameter connected to the first shaft 58, a second shaft 62 provided coaxially with the output shaft 30, a secondary pulley 64 having a variable effective diameter connected to the second shaft 62, and a transmission belt 66 as a transmission element wound between these pulleys 60, 64. The continuously variable transmission 24 is a known belt-type continuously variable transmission that transmits power via frictional force between the pulleys 60 and 64 and the transmission belt 66, and transmits power of the engine 12 to the drive wheels 14. The primary pulley 60 has its effective diameter changed by a hydraulic actuator 60a, and the secondary pulley 64 has its effective diameter changed by a hydraulic actuator 64 a.

In the power transmission device 16, the power transmission path PT that transmits the power of the engine 12 to the drive wheels 14 is switched between the first power transmission path PT1 and the second power transmission path PT2 according to the running state of the vehicle 10. Therefore, the power transmission device 16 includes a plurality of engagement devices for selectively forming the first power transmission path PT1 and the second power transmission path PT 2. The plurality of engaging devices includes a first clutch C1, a first brake B1, a second clutch C2, and a two-way clutch TWC.

The first clutch C1 is an engagement device that is provided on the first power transmission path PT1 and selectively connects or disconnects the first power transmission path PT1, and is an engagement device that enables the first power transmission path PT1 to transmit power by engagement when the vehicle travels forward. The first brake B1 is an engagement device provided on the first power transmission path PT1 and selectively connecting or disconnecting the first power transmission path PT1, and is an engagement device that transmits power along the first power transmission path PT1 by engagement when the vehicle travels backward. The first power transmission path PT1 is formed by engagement of the first clutch C1 or the first brake B1.

The two-way clutch TWC is provided on the first power transmission path PT1, and is configured to be switchable between a one-way mode in which power is transmitted in a driving state of the vehicle 10 during forward travel and power is cut off in a driven state of the vehicle 10 during forward travel and a lock-up mode in which power is transmitted in the driving state and the driven state of the vehicle 10. For example, in a state where the first clutch C1 is engaged and the two-way clutch TWC is switched to the one-way mode, the two-way clutch TWC can transmit power in a driving state of the vehicle 10 in which the vehicle travels forward by the power of the engine 12. That is, during the forward travel, the power of the engine 12 is transmitted to the drive wheels 14 via the first power transmission path PT 1. On the other hand, during coasting or the like, even if the first clutch C1 is engaged in the driven state of the vehicle 10, the rotation transmitted from the drive wheels 14 side is interrupted by the two-way clutch TWC. The driving state of the vehicle 10 is a state in which the torque of the input shaft 22 is a positive value with respect to the traveling direction, and substantially corresponds to a state in which the vehicle 10 is driven by the power of the engine 12. The driven state of the vehicle 10 is a state in which the torque of the input shaft 22 is a negative value with respect to the traveling direction, and substantially corresponds to a state in which the engine 12 is caused to rotate by the rotation transmitted from the drive wheels 14 side while traveling by the inertia of the vehicle 10.

Further, in the state where the first clutch 1 is engaged and the two-way clutch TWC is switched to the lock-up mode, the two-way clutch TWC is capable of power transmission in the driving state and the driven state of the vehicle 10, so that the power of the engine 12 is transmitted to the drive wheels 14 side via the first power transmission path PT1, and during the inertia running (driven state), the rotation transmitted from the drive wheels 14 side is transmitted to the engine 12 side via the first power transmission path PT1, so that the engine brake can be generated by the engine 12 being rotated by the engine 12. Further, in a state where the first brake B1 is engaged and the two-way clutch TWC is switched to the lock-up mode, the power acting in the vehicle reverse direction, which is transmitted from the engine 12 side, is transmitted to the drive wheels 14 via the two-way clutch TWC, and reverse travel via the first power transmission path PT1 can be disabled. The structure of the two-way clutch TWC will be described later.

The second clutch C2 is an engagement device that is provided on the second power transmission path PT2 and selectively connects or couples the second power transmission path PT2, and is engaged to enable the second power transmission path PT2 to transmit power when the vehicle travels forward. The first clutch C1, the first brake B1, and the second clutch C2 are each a known hydraulic wet friction engagement device that is frictionally engaged by a hydraulic actuator. The first clutch C1 and the first brake B1 are each one of elements constituting the forward/reverse switching device 26.

The engine 12 includes an engine control device 42, and the engine control device 42 includes various devices necessary for output control of the engine 12, such as an electronic throttle device, a fuel injection device, and an ignition device. The engine 12 controls an engine torque Te, which is an output torque of the engine 12, by controlling the engine control device 42 based on an accelerator operation amount θ acc, which is an operation amount of the accelerator pedal 45 corresponding to a drive request amount for the vehicle 10 by a driver, by the electronic control device 100 described later.

The torque converter 20 includes a pump impeller 20p that is provided between the engine 12 and the continuously variable transmission 24 and the forward/reverse switching device 26 and is coupled to the engine 12, and a turbine runner 20t that is coupled to the input shaft 22. The torque converter 20 is a fluid transmission device that transmits power of the engine 12 to the input shaft 22. The torque converter 20 includes a known lock-up clutch LU that can directly couple the pump impeller 20p and the turbine runner 20t, that is, the input/output rotating member of the torque converter 20. The lockup clutch LU directly couples the pump impeller 20p and the turbine impeller 20t (i.e., between the engine 12 and the input shaft 22) according to the traveling state of the vehicle. For example, in the high vehicle speed region, the engine 12 is directly coupled to the input shaft 22 via the lock-up clutch LU.

The power transmission device 16 includes a mechanical oil pump 44 connected to the pump impeller 20 p. The oil pump 44 is rotationally driven by the engine 12, and supplies a source pressure of an operating fluid pressure for performing an operation, such as a shift control of the continuously variable transmission 24, generation of a belt clamping force in the continuously variable transmission 24, switching of an operating state, such as engagement or release of each of the plurality of engagement devices, or switching of an operating state of the lockup clutch LU, to a fluid pressure control circuit 46 provided in the vehicle 10.

The forward/reverse switching device 26 includes a double-pinion planetary gear device 26p, a first clutch C1, and a first brake B1. The planetary gear device 26p is a differential mechanism having three rotation elements, i.e., a carrier 26c as an input element, a sun gear 26s as an output element, and a ring gear 26r as a reaction element. The carrier 26c is coupled to the input shaft 22. The ring gear 26r is selectively coupled to the housing 18 via the first brake B1. The sun gear 26s is disposed on the outer peripheral side of the input shaft 22, and is connected to a small-diameter gear 48 provided to be rotatable relative to the input shaft 22. The carrier 26C and the sun gear 26s are selectively coupled via a first clutch C1.

The gear mechanism 28 includes a small-diameter gear 48, a counter shaft 50, and a large-diameter gear 52 provided on the counter shaft 50 to be relatively rotatable and meshing with the small-diameter gear 48. Further, a counter gear 54 that meshes with an output gear 56 provided on the output shaft 30 is provided on the counter shaft 50 so as not to be relatively rotatable with respect to the counter shaft 50.

A two-way clutch TWC is provided between the large diameter gear 52 and the counter gear 54 in the axial direction of the counter shaft 50. The two-way clutch TWC is provided on the drive wheel 14 side of the first clutch C1 and the gear mechanism 28 on the first power transmission path PT 1. The two-way clutch TWC is switched to one of the one-way mode and the lock-up mode by a hydraulic actuator 41 provided adjacent to the counter shaft 50 in the axial direction.

Fig. 2 and 3 are views schematically showing the structure of the two-way clutch TWC that can switch between the one-way mode and the lock-up mode, and are cross-sectional views obtained by cutting a part of the two-way clutch TWC in the circumferential direction. Fig. 2 shows a state where the two-way clutch TWC is switched to the one-way mode, and fig. 3 shows a state where the two-way clutch TWC is switched to the lock-up mode. In fig. 2 and 3, the vertical direction on the paper corresponds to the rotation direction, the upward direction on the paper corresponds to the vehicle backward direction (backward rotation direction), and the downward direction on the paper corresponds to the vehicle forward direction (forward rotation direction). The left-right direction of the paper of fig. 2 and 3 corresponds to the axial direction of the counter shaft 50 (hereinafter, unless otherwise noted, the axial direction corresponds to the axial direction of the counter shaft 50), the right side of the paper corresponds to the large diameter gear 52 side of fig. 1, and the left side of the paper corresponds to the counter gear 54 side of fig. 1.

The two-way clutch TWC is formed in a disk shape and is disposed on the outer peripheral side of the counter shaft 50. The two-way clutch TWC includes an input-side rotating member 68, a first output-side rotating member 70a and a second output-side rotating member 70b that are disposed at positions adjacent to the input-side rotating member 68 in the axial direction, a plurality of first support plates 72a and a plurality of torsion coil springs 73a that are inserted between the input-side rotating member 68 and the first output-side rotating member 70a in the axial direction, and a plurality of second support plates 72b and a plurality of torsion coil springs 73b that are inserted between the input-side rotating member 68 and the second output-side rotating member 70b in the axial direction. The first output side rotation member 70a and the second output side rotation member 70b correspond to the output side rotation member of the present invention.

The input-side rotary member 68 is formed in a disk shape and is disposed so as to be rotatable relative to the counter shaft 50 about the axial center of the counter shaft 50. The input-side rotating member 68 is disposed so as to be sandwiched between the first output-side rotating member 70a and the second output-side rotating member 70b in the axial direction. Further, on the outer peripheral side of the input-side rotating member 68, meshing teeth of the large-diameter gear 52 are integrally formed. That is, the input-side rotating member 68 and the large-diameter gear 52 are integrally formed. The input-side rotating member 68 is coupled to the engine 12 via the gear mechanism 28, the forward/reverse switching device 26, and the like so as to be capable of transmitting power.

A first housing portion 76a that houses the first support plate 72a and the torsion coil spring 73a is formed on a surface of the input-side rotating member 68 that faces the first output-side rotating member 70a in the axial direction. The first receiving portion 76a is formed in plurality at equal angular intervals in the circumferential direction. A second housing portion 76b that houses the second support plate 72b and the torsion coil spring 73bd is formed on a surface of the input-side rotating member 68 that faces the second output-side rotating member 70b in the axial direction. The second receiving portions 76b are formed in plurality at equal angular intervals in the circumferential direction. The first housing portion 76a and the second housing portion 76b are formed at the same position in the radial direction of the input-side rotating member 68.

The first output side rotation member 70a is formed in a disk shape and is disposed so as to be rotatable about the axial center of the counter shaft 50. The first output side rotating member 70a is provided on the counter shaft 50 so as to be relatively non-rotatable, and thus rotates integrally with the counter shaft 50. In association with this, the first output-side rotating member 70a is coupled to the drive wheels 14 via the counter shaft 50, the counter gear 54, the output shaft 30, the differential device 38, and the like so as to be able to transmit power.

A first recess 78a that is recessed in a direction away from the input-side rotating member 68 is formed in a surface of the first output-side rotating member 70a that faces the input-side rotating member 68 in the axial direction. The first recesses 78a are formed in the same number as the first receiving portions 76a, and are arranged at equal angular intervals in the circumferential direction. Further, the first recess 78a is formed at the same position as the first housing portion 76a in the radial direction of the first output side rotating member 70a, the first housing portion 76a being formed on the input side rotating member 68. Therefore, when the rotational positions of the first housing portion 76a and the first recess portion 78a are matched, the first housing portions 76a and the first recess portions 78a are adjacent to each other in the axial direction. The first recess 78a is shaped to receive one end of the first support plate 72 a. Further, at one end in the circumferential direction of the first recess 78a, when the input-side rotating member 68 (which is opposed to the output-side rotating member 70) is rotated in the vehicle forward direction (downward in the paper plane in fig. 2 and 3) by the power of the engine 12, a first wall surface 80a is formed which abuts one end of the first support plate 72 a.

The second output side rotation member 70b is formed in a disk shape and is disposed so as to be rotatable about the axial center of the counter shaft 50. The second output side rotating member 70b is provided on the counter shaft 50 so as to be relatively non-rotatable, and thus rotates integrally with the counter shaft 50. In association with this, the second output side rotating member 70b is coupled to the drive wheels 14 via the counter shaft 50, the counter gear 54, the output shaft 30, the differential device 38, and the like so as to be able to transmit power.

A second recess 78b that is recessed in a direction away from the input-side rotating member 68 is formed in a surface of the second output-side rotating member 70b that faces the input-side rotating member 68 in the axial direction. The second recesses 78b are formed in the same number as the second receiving portions 76b, and are arranged at equal angular intervals in the circumferential direction. Further, the second recess 78b is formed at the same position as the second housing portion 76b in the radial direction of the second output side rotating member 70b, the second housing portion 76b being formed on the input side rotating member 68. Therefore, when the rotational positions of the second housing portion 76b and the second recess portion 78b are matched, the second housing portions 76b and the second recess portions 78b are adjacent to each other in the axial direction. The second recess 78b is shaped to receive one end of the second support plate 72 b. Further, at one end in the circumferential direction of the second recess 78b, a second wall surface 80b is formed which abuts one end of the second support plate 72b when the input-side rotating member 68 (which is opposed to the output-side rotating member 70) is rotated in the vehicle backward direction (upward in the paper plane in fig. 2 and 3) by the power of the engine 12 in a state where the two-way clutch TWC shown in fig. 3 is switched to the lockup mode, that is, when the vehicle is traveling backward or when the vehicle is traveling by inertia during forward traveling.

The first support plate 72a is formed of a plate-like member having a predetermined thickness, and is formed in an elongated shape along the rotation direction (the paper surface vertical direction) as shown in the cross sections of fig. 2 and 3. Further, the first support plate 72a has a predetermined size in a direction perpendicular to the paper surface in fig. 2 and 3.

One end of the first support plate 72a in the longitudinal direction is biased toward the first output side rotating member 70a by a torsion coil spring 73 a. The other end of the first support plate 72a in the longitudinal direction abuts against a first additional step 82a formed in the first housing portion 76 a. The first support plate 72a can rotate about the other end abutting the first additional step 82 a. The torsion coil spring 73a is interposed between the first support plate 72a and the input-side rotating member 68, and urges one end of the first support plate 72a toward the first output-side rotating member 70 a.

With the above configuration, when power acting in the vehicle forward direction is transmitted from the engine 12 side while the two-way clutch TWC is switched between the one-way mode and the lock-up mode, one end of the first support plate 72a abuts against the first wall surface 80a of the first output-side rotating member 70a, and the other end of the first support plate 72a abuts against the first additional step portion 82a of the input-side rotating member 68. In this state, the relative rotation of the input side rotating member 68 and the first output side rotating member 70a is prevented, and the power acting in the vehicle forward direction is transmitted to the drive wheels 14 side via the two-way clutch TWC. The first support plate 72a, the torsion coil spring 73a, the first housing portion 76a, and the first recess 78a (the first wall surface 80a) constitute a one-way clutch that transmits power acting in the forward direction of the vehicle to the drive wheels 14 and cuts off power acting in the reverse direction of the vehicle.

The second support plate 72b is formed of a plate-like member having a predetermined thickness, and is formed in an elongated shape along the rotation direction (the paper surface vertical direction) as shown in the cross sections of fig. 2 and 3. Further, the second support plate 72b has a predetermined size in a direction perpendicular to the paper surface in fig. 2 and 3.

One end of the second support plate 72b in the longitudinal direction is biased toward the second output side rotating member 70b by a torsion coil spring 73 b. The other end of the second support plate 72b in the longitudinal direction abuts against a second additional step 82b formed in the second housing portion 76 b. The second support plate 72b can rotate about the other end abutting against the second additional step portion 82 b. The torsion coil spring 73b is interposed between the second support plate 72b and the input-side rotating member 68, and biases one end of the second support plate 72b toward the second output-side rotating member 70 b.

With the above configuration, when power acting in the vehicle reverse direction is transmitted from the engine 12 side to the second support plate 72b in the state where the two-way clutch TWC is switched to the lock-up mode, one end of the second support plate 72b abuts against the second wall surface 80b of the second output-side rotating member 70b, and the other end of the second support plate 72b abuts against the second additional stepped portion 82b of the input-side rotating member 68. Even when the inertia running is performed during the forward running, one end of the second support plate 72b abuts against the second wall surface 80b of the second output-side rotating member 70b, and the other end of the second support plate 72b abuts against the second additional step 82b of the input-side rotating member 68. In this state, the relative rotation between the input side rotating member 68 and the second output side rotating member 70b is prevented, and the power acting in the vehicle reverse direction is transmitted to the drive wheels 14 via the two-way clutch TWC. Further, the rotation transmitted from the driving wheel 14 side during the inertia running is transmitted to the engine 12 side via the two-way clutch TWC. The second support plate 72b, the torsion coil spring 73b, the second housing portion 76b, and the second recess 78b (the second wall surface 80b) constitute a one-way clutch that transmits power acting in the vehicle reverse direction to the drive wheels 14 and cuts off power acting in the vehicle forward direction.

Further, the second output side rotating member 70b is formed with a plurality of through holes 88 that penetrate the second output side rotating member 70b in the axial direction. The through holes 88 are formed at positions overlapping the second concave portions 78b when viewed in the axial direction of the counter shaft 50. Therefore, one end of each through-hole 88 communicates with the second recess 78 b. A pin 90 is inserted into each through hole 88. The pin 90 is formed in a cylindrical shape and is slidable in the through hole 88. One end of the pin 90 abuts against the pressing plate 74 constituting the hydraulic actuator 41, and the other end of the pin 90 abuts against the annular ring 86 having a part in the circumferential direction passing through the second recess 78 b.

A ring 86 is fitted in the plurality of circular arc-shaped channel portions 84, and allows relative movement with respect to the second output side rotation member 70b in the axial direction, and the plurality of circular arc-shaped channel portions 84 are formed on the second output side rotation member 70b and are formed so as to connect circumferentially adjacent second concave portions 78 b.

The hydraulic actuator 41 is disposed on the same counter shaft 50 as the two-way clutch TWC, and is disposed at a position adjacent to the second output side rotating member 70b in the axial direction of the counter shaft 50. The hydraulic actuator 41 includes a pressing plate 74, a plurality of coil springs 92 interposed between the counter gear 54 and the pressing plate 74 in the axial direction, and a hydraulic chamber, not shown, for generating a thrust force to move the pressing plate 74 toward the counter gear 54 in the axial direction by supplying hydraulic oil.

The pressing plate 74 is formed in a disc shape and is disposed so as to be movable relative to the counter shaft 50 in the axial direction. The spring 92 urges the pressing portion 74 toward the second output-side rotating member 70b side in the axial direction. Therefore, in a state where the hydraulic oil is not supplied to the hydraulic chamber of the hydraulic actuator 41, as shown in fig. 2, the pressing plate 74 is moved in the axial direction toward the second output side rotation member 70b by the urging force of the spring 92, and the pressing plate 74 is brought into contact with the second output side rotation member 70 b. At this time, as shown in fig. 2, the two-way clutch TWC is switched to the one-way mode by the pin 90, the ring 86, and the one end of the second support plate 72b moving toward the input-side rotating member 68 side in the axial direction.

When the hydraulic oil is supplied to the hydraulic chamber of the hydraulic actuator 41, the pressing plate 74 moves in the axial direction toward the counter gear 54 against the biasing force of the spring 92, and the pressing plate 74 is in a state of being separated from the second output-side rotating member 70 b. At this time, as shown in fig. 3, the pin 90, the ring 86, and one end of the second support plate 72b are moved in the axial direction toward the counter gear 54 side by the urging force of the torsion coil spring 73b, and the bidirectional clutch TWC is switched to the lock-up mode.

In a state where the two-way clutch TWC shown in fig. 2 is in the one-way mode, the pressing plate 74 abuts against the second output side rotating member 70b by the urging force of the spring 92. At this time, the pin 90 is pressed by the pressing plate 74 and moves toward the input-side rotating member 68 in the axial direction, and the ring 86 is also pressed by the pin 90 and moves toward the input-side rotating member 68 in the axial direction. As a result, the one end of the second support plate 72b is pressed by the ring 86 and moves toward the input-side rotating member 68, so that the one end of the second support plate 72b is prevented from abutting against the second wall surface 80 b. At this time, relative rotation between the input-side rotating member 68 and the second output-side rotating member 70b is permitted, and the second support plate 72b does not function as a one-way clutch. On the other hand, since the one end of the first support plate 72a is biased toward the first output side rotating member 70a by the torsion coil spring 73a and can come into contact with the first wall surface 80a of the first concave portion 78a, the first support plate 72a functions as a one-way clutch that transmits the driving force acting in the vehicle forward direction.

Since the one end of the first support plate 72a can abut against the first wall surface 80a of the first output side rotating member 70a in the state where the two-way clutch TWC shown in fig. 2 is in the one-way mode, when the vehicle 10 is in the driving state where the power acting in the vehicle forward direction is transmitted from the engine 12 to the two-way clutch TWC, as shown in fig. 2, the one end of the first support plate 72a abuts against the first wall surface 80a and the other end of the first support plate 72a abuts against the first stepped portion 82a, so that the relative rotation in the vehicle forward direction is prevented between the input side rotating member 68 and the first output side rotating member 70a, whereby the power of the engine 12 is transmitted to the drive wheels 14 via the two-way clutch TWC. On the other hand, when the vehicle 10 is driven by the inertia running during the forward running, the one end of the first support plate 72a does not abut against the first wall surface 80a of the first output-side rotating member 70a, and the relative rotation between the input-side rotating member 68 and the first output-side rotating member 70a is allowed, so that the power transmission via the two-way clutch TWC is interrupted. Therefore, in the state where the two-way clutch TWC is in the one-way mode, the first support plate 72a functions as a one-way clutch, and power is transmitted in the driving state of the vehicle 10 in which power acting in the vehicle forward direction is transmitted from the engine 12, whereas power is cut off in the driven state of the vehicle 10 in which inertia running is performed during forward running.

In the state where the two-way clutch TWC shown in fig. 3 is in the lock-up mode, the hydraulic oil is supplied to the hydraulic chamber of the hydraulic actuator 41, whereby the pressing plate 74 moves in the direction away from the second output side rotating member 70b against the urging force of the spring 92. At this time, one end of the second support plate 72b can move toward the second recess 78b of the second output side rotation member 70b by the biasing force of the torsion coil spring 73b, and can come into contact with the second wall surface 80 b. Further, as in the unidirectional mode of fig. 2, the first support plate 72a can also have one end that abuts the first wall surface 80a of the first output-side rotating member 70 a.

When power acting in the forward direction of the vehicle is transmitted in a state where the two-way clutch TWC shown in fig. 3 is in the lock-up mode, relative rotation between the input-side rotating member 68 and the first output-side rotating member 70a in the forward direction of the vehicle is prevented by one end of the first support plate 72a abutting against the first wall surface 80a of the first output-side rotating member 70a and the other end of the first support plate 72a abutting against the first additional step portion 82 a. When the power acting in the vehicle reverse direction is transmitted in the state where the two-way clutch TWC is in the lock-up mode, as shown in fig. 3, the one end of the second support plate 72b abuts against the second wall surface 80b of the second output-side rotating member 70b, and the other end of the second support plate 72b abuts against the second additional step portion 82b, so that the relative rotation in the vehicle reverse direction is prevented between the input-side rotating member 68 and the second output-side rotating member 70 b. Therefore, in the state where the two-way clutch TWC is in the lock-up mode, the first support plate 72a and the second support plate 72b function as one-way clutches, respectively, and the power acting in the vehicle forward direction and the vehicle reverse direction can be transmitted to the drive wheels 14 in the two-way clutch TWC. Therefore, when the vehicle is moving backward, the two-way clutch TWC is switched to the lock-up mode, so that backward travel is possible. Further, in the driven state of the vehicle 10 that is subjected to inertia running during forward running of the vehicle, by causing the two-way clutch TWC to be switched to the lock-up mode, the rotation transmitted from the drive wheel 14 side is transmitted to the engine 12 side via the two-way clutch TWC, so that the engine brake due to the engine 12 being rotated with the rotation can be generated. Therefore, in the state where the two-way clutch TWC is in the lock-up mode, the first support plate 72a and the second support plate 72b function as one-way clutches, and power is transmitted in the driving state and the driven state of the vehicle 10.

Fig. 4 is an engagement operation table showing engagement states of the engagement devices at respective operation positions POSsh selected as a shift lever 98 of a shift switching device provided in the vehicle 10, in fig. 4, "C1" corresponds to the first clutch C1, "C2" corresponds to the second clutch C2, "B1" corresponds to the first brake B1, and "TWC" corresponds to the two-way clutch TWC, and "P (P position)", "R (R position)", "N (N position)", "D (D position)" and "M (M position)" show the respective operation positions POSsh selected by the shift lever 98, and "○" in fig. 4 shows engagement of the respective engagement devices, and a blank bar shows release, and "tw ○" shows switching of the two-way clutch C to the lock mode, and a blank bar shows switching of the two-way clutch TWC to the one-way mode.

For example, when the operating position POSsh of the shift lever 98 is switched to the P position, which is the vehicle stop position, or the N position, which is the power transmission cut-off position, as shown in fig. 4, the first clutch C1, the second clutch C2, and the first brake B1 are released. At this time, the first power transmission path PT1 and the second power transmission path PT2 are both in a neutral state in which power is not transmitted.

Further, when the operating position POSsh of the shift lever 98 is switched to the R position, which is the reverse travel position, as shown in fig. 4, the first brake B1 is engaged, and the two-way clutch TWC is switched to the lock-up mode. The first brake B1 is engaged, and power acting in the reverse direction is transmitted from the engine 12 side to the gear mechanism 28. At this time, when the two-way clutch TWC is in the one-way mode, the power is cut off by the two-way clutch TWC, and therefore, the reverse travel cannot be performed. Therefore, since the power acting in the vehicle reverse direction is transmitted to the output shaft 30 side via the two-way clutch TWC by the two-way clutch TWC being switched to the lock-up mode, reverse travel is possible. Therefore, when the operating position POSsh is switched to the R position, the first brake B1 is engaged, and the two-way clutch TWC is switched to the lock-up mode, whereby a reverse gear stage is formed in which power in the vehicle reverse direction is transmitted via the first power transmission path PT1 (gear mechanism 28).

When the operating position POSsh of the shift lever 98 is switched to the D position, which is the forward travel position, the first clutch C1 is engaged or the second clutch C2 is engaged as shown in fig. 4. "D1 (D1 position)" and "D2 (D2 position)" shown in fig. 4 are virtual operation positions that are controllably set, and when the operation position POSsh is switched to the D position, the operation position POSsh is automatically switched to the D1 position or the D2 position depending on the running state of the vehicle 10. The D1 position is switched in a low vehicle speed region including during vehicle stop. The D2 position is switched in a high vehicle speed region including a medium vehicle speed region. For example, when the traveling state of the vehicle 10 moves from a low vehicle speed region to a high vehicle speed region while traveling at the D position, the position is automatically switched from the D1 position to the D2 position.

For example, when the operation position POSsh is switched to the D position, the first clutch C1 is engaged and the second clutch C2 is released when the running state of the vehicle 10 is in the running region corresponding to the D1 position. At this time, the vehicle is in the gear running mode in which the power acting in the forward direction of the vehicle is transmitted from the engine 12 side to the drive wheels 14 via the first power transmission path PT1 (gear mechanism 28). In addition, since the two-way clutch TWC is switched to the one-way mode, the power acting in the forward direction of the vehicle is transmitted.

Further, when the operation position POSsh is switched to the D position, the first clutch C1 is released and the second clutch C2 is engaged when the running state of the vehicle 10 is in the running region corresponding to the D2 position. At this time, the belt running mode is established in which the power acting in the forward direction is transmitted from the engine 12 side to the drive wheels 14 via the second power transmission path PT2 (continuously variable transmission 24). When the operation position POSsh is switched to the D position in this way, the power of the engine 12 is transmitted to the drive wheels 14 via the first power transmission path PT1 (gear mechanism 28) or the second power transmission path PT2 (continuously variable transmission 24) according to the running state of the vehicle 10.

When the operation position POSsh of shift lever 98 is switched to the M position, the shift can be switched to the upshift and the downshift by the manual operation of the driver. That is, the M position is a manual shift position where a shift can be performed by a manual operation of the driver. For example, when the driver manually operates the shift-down side in the state where the operation position POSsh is switched to the M position, a forward gear stage is formed in which the first clutch C1 is engaged and the two-way clutch TWC is switched to the lockup mode. Further, by the two-way clutch TWC being switched to the lock-up mode, power transmission can be performed in both the driving state and the driven state of the vehicle 10 in the two-way clutch TWC. For example, although the vehicle is in a driven state in which rotation is transmitted from the drive wheels 14 during the inertia running, when the vehicle is manually operated to the downshift side at the M position, the rotation transmitted from the drive wheels 14 is transmitted to the engine 12 via the two-way clutch TWC, so that the engine 12 is rotated by being rotated, and the engine brake can be generated. In this way, when the operating position POSsh is shifted down at the M position, power is transmitted to the drive wheels 14 via the first power transmission path PT1 (gear mechanism 28), and during the inertia running, a forward gear stage is formed in which engine braking can be generated by the rotation transmitted from the drive wheels 14 side being transmitted to the engine 12 side via the first power transmission path PT 1.

When the driver manually operates the shift lever 98 to the upshift side with the operating position POSsh switched to the M position, the second clutch C2 is engaged. At this time, a forward continuously variable shift stage is formed in which power is transmitted to the drive wheels 14 via the second power transmission path PT2 (continuously variable transmission 24). In this way, when the operation position POSsh is switched to the M position, the driver can perform manual shift by manual operation to switch between a forward gear stage (i.e., a gear running mode) in which power is transmitted via the first power transmission path PT1 and a forward continuously variable gear stage (i.e., a belt running mode) in which power is transmitted via the second power transmission path PT 2. In addition, the case where the operation position POSsh is shifted down at the M position corresponds to the M1 position of fig. 4, and the case where the operation position POSsh is shifted up at the M position corresponds to the M2 position of fig. 4. Although these M1 position and M2 position do not exist on the surface, hereinafter, in the case where the operation position POSsh is manually operated to the down shift side at the M position, it is briefly described as being switched to the M1 position, and in the case where the operation position POSsh is manually operated to the up shift side at the M position, it is briefly described as being switched to the M2 position.

Returning to fig. 1, the vehicle 10 includes an electronic control device 100 as a controller including a control device of the power transmission device 16. The electronic control device 100 is configured to include a so-called microcomputer including, for example, a CPU, a RAM, a ROM, an input/output interface, and the like, and the CPU executes various kinds of control of the vehicle 10 by executing signal processing in accordance with a program stored in advance in the ROM while utilizing a temporary storage function of the RAM. The electronic control device 100 executes output control of the engine 12, shift control or belt clamping pressure control of the continuously variable transmission 24, hydraulic pressure control for switching the respective operation states of the plurality of engagement devices (C1, B1, C2, TWC), and the like. The electronic control device 100 is configured to be divided into an engine control device, a hydraulic control device, and the like as necessary.

The electronic control device 100 is supplied with various detection signals and the like (for example, an engine rotation speed Ne, a first rotation speed Npri and a second rotation speed Nsec which are equal to an input shaft rotation speed Nin, an output shaft rotation speed Nout corresponding to a vehicle speed V, an input rotation speed nwcin of the input side rotating member 68 constituting the two-way clutch TWC, an accelerator operation amount θ acc of the accelerator pedal 45 indicating the magnitude of an accelerator operation by the driver, a throttle opening tap, an operation position POSsh of the shift lever 98 as a shift switching device provided in the vehicle 10, an operating oil temperature THoil as the temperature of the operating oil in the hydraulic control circuit 46, and the like) which are transmitted from various sensors and the like (for example, various

rotation speed sensors

102, 104, 106, 108, 109, an accelerator operation amount sensor 110, a throttle opening sensor 112, a shift position sensor 114, an oil temperature sensor 116 and the like) provided in the vehicle 10). The input shaft speed Nin (first speed Npri) is also the turbine speed NT. Further, the electronic control device 100 calculates an actual speed ratio γ cvt (Npri/Nsec) which is an actual speed ratio γ cvt of the continuously variable transmission 24, based on the first rotation speed Npri and the second rotation speed Nsec. The electronic control device 100 calculates an output rotation speed Ntwcout of a first output-side rotating member 70a and a second output-side rotating member 70b (hereinafter, referred to as the output-side rotating member 70 unless otherwise specified) constituting the two-way clutch TWC, based on the output shaft rotation speed Nout.

Various command signals (for example, an engine control command signal Se for controlling the engine 12, a hydraulic control command signal Scvt for controlling the gear shift, the belt clamping pressure, and the like of the continuously variable transmission 24, a hydraulic control command signal Scbd for controlling the respective operation states of the plurality of engagement devices, a hydraulic control command signal Slu for controlling the operation state of the lock-up clutch LU, and the like) are output from the electronic control device 100 to the respective devices (for example, the engine control device 42, the hydraulic control circuit 46, and the like) provided in the vehicle 10.

Upon receiving these various command signals, the hydraulic control circuit 46 outputs SL1 hydraulic pressure Psl1, which is the hydraulic pressure supplied to the hydraulic actuator of the first clutch C1, B1 control pressure Pb1, which is the hydraulic pressure supplied to the hydraulic actuator of the first brake B1, SL2 hydraulic pressure Psl2, which is the hydraulic pressure supplied to the hydraulic actuator of the second clutch C2, TWC hydraulic pressure Ptwc, which is the hydraulic pressure supplied to the hydraulic actuator 41 that switches the mode of the two-way clutch TWC, line pressure Ppri, which is supplied to the hydraulic actuator 60a of the primary pulley 60, secondary pressure Psec, which is supplied to the hydraulic actuator 64a of the secondary pulley 64, LU pressure Plu, which controls the lockup clutch LU, and the like. The SL1 hydraulic pressure Psl1, the SL2 hydraulic pressure Psl2, and the B1 control pressure Pb1, the TWC hydraulic pressure Ptwc, the line pressure Ppri, the secondary pressure Psec, and the LU pressure Plu are directly or indirectly regulated by solenoid valves, not shown, provided in the hydraulic control circuit 46.

In order to implement various controls in the vehicle 10, the electronic control device 100 functionally includes an engine control unit 120 that functions as an engine control means and a shift control unit 122 that functions as a shift control means.

The engine control unit 120 calculates the required driving force Fdem by applying the accelerator operation amount θ acc and the vehicle speed V to, for example, a driving force map that is a predetermined relationship that is a relationship that is experimentally or designably obtained and stored in advance. The engine control unit 120 sets a target engine torque Tet at which the required driving force Fdem is obtained, and outputs a command for controlling the engine 12 so as to obtain the target engine torque Tet to the engine control device 42.

For example, when the operating position POSsh is switched from the P position or the N position to the D position during the stop of the vehicle, the shift control unit 122 outputs a command to engage the first clutch C1 to the hydraulic control circuit 46. Thereby, the vehicle 10 is switched to the forward gear running mode in which forward running is possible via the first power transmission path PT 1. When the operating position POSsh is switched from the P position or the N position to the R position during the stop of the vehicle, the shift control unit 122 engages the first brake B1 and outputs a command to switch the two-way clutch TWC to the lockup mode to the hydraulic control circuit 46. Thereby, the vehicle 10 is switched to the reverse gear drive mode in which the reverse drive can be performed via the first power transmission path PT 1.

Further, the shift control unit 122 outputs a command for controlling the gear ratio γ of the continuously variable transmission 24 so as to be a target gear ratio γ tgt calculated from the accelerator opening degree θ acc, the vehicle speed V, and the like, to the hydraulic control circuit 46 during traveling in the belt traveling mode via, for example, the second power transmission path PT 2. Specifically, the shift control portion 122 stores a predetermined relationship (for example, a shift map) of the target gear ratio γ tgt of the continuously variable transmission 24 that achieves that the operating point of the engine 12 becomes a predetermined optimum line (for example, an engine optimum fuel consumption line) while adjusting the belt clamping pressure of the continuously variable transmission 24 to an optimum value, determines a primary pilot pressure Ppritgt, which is a command value of the primary pressure Ppri supplied to the hydraulic actuator 60c of the primary pulley 60, and a secondary pilot pressure Psectgt, which is a command value of the secondary pressure Psec supplied to the hydraulic actuator 64a of the secondary pulley 64, based on the accelerator operation amount θ acc, the vehicle speed V, and the like, based on the relationship, and outputs commands for controlling the primary pressure Ppri and the secondary pressure Psec to the hydraulic control circuit 46 so as to become the primary pilot pressure Ppritgt and the secondary pilot pressure Psectgt, thereby performing the shifting of the continuously variable transmission 24. Since the shift control of the continuously variable transmission 24 is a well-known technique, a detailed description thereof will be omitted.

Further, the shift control unit 122 executes switching control for switching between the gear running mode and the belt running mode when the operation position POSsh is the D position. Specifically, the shift control unit 122 stores a shift map that is a predetermined relationship for switching between a first-speed gear shift stage corresponding to the gear ratio EL of the gear mechanism 28 in the gear running mode and a second-speed gear shift stage corresponding to the lowest-side gear ratio γ max of the continuously variable transmission 24 in the belt running mode. The shift map is configured by the vehicle speed V, the accelerator operation amount θ acc, and the like, and an upshift line for determining switching to the belt travel mode, which is an upshift of the second-speed gear position, and a downshift line for determining switching to the gear travel mode, which is a downshift of the first-speed gear position, are set on the shift map. The shift control unit 122 determines whether or not a shift is necessary by applying the actual vehicle speed V and the accelerator operation amount θ acc to the shift map, and executes the shift (i.e., switching of the running mode) in accordance with the determination result. For example, when a downshift line is crossed during traveling in the belt travel mode, it is determined that a downshift (downshift request) is made to the first-speed gear stage (gear travel mode), and when an upshift line is crossed during traveling in the gear travel mode, it is determined that an upshift (upshift request) is made to the second-speed gear stage (belt travel mode). In addition, the gear running mode corresponds to the position D1 of fig. 4, and the belt running mode corresponds to the position D2 of fig. 4.

For example, when a downshift request to switch the shift control unit 122 to the gear drive mode (corresponding to the D1 position) is satisfied during the drive in the belt drive mode (corresponding to the D2 position) in which the operation position POSsh is the D position, a command to engage the first clutch C1 and release the second clutch C2 is output to the hydraulic control circuit 46. Thereby, the power transmission path PT in the power transmission device 16 is switched from the second power transmission path PT2 to the first power transmission path PT 1. That is, the first power transmission path PT1 is provided to enable power transmission. In this way, the shift control unit 122 switches the power transmission path PT from the belt running mode in which power is transmitted via the second power transmission path PT2 to the gear running mode in which power is transmitted via the first power transmission path PT1 by the stepped shift control (downshift control) by engagement of the first clutch C1 and release of the second clutch C2.

When an upshift request to switch to the belt drive mode (corresponding to the D2 position) is established while the shift control unit 122 is traveling in the gear drive mode (corresponding to the D1 position) in which the operation position POSsh is the D position, a command to release the first clutch C1 and engage the second clutch C2 is output to the hydraulic control circuit 46. Thereby, the power transmission path PT in the power transmission device 16 is switched from the first power transmission path PT1 to the second power transmission path PT 2. That is, the second power transmission path PT2 is provided to be able to transmit power. In this way, the shift control unit 122 switches the power transmission path PT from the gear running mode in which power is transmitted via the first power transmission path PT1 to the belt running mode in which power is transmitted via the second power transmission path PT2 by the stepped shift control (upshift control) by the release of the first clutch C1 and the engagement of the second clutch C2.

When the running mode of the vehicle 10 is switched to the belt running mode, power is transmitted via the second power transmission path PT2 (continuously variable transmission 24) in the power transmission device 16. At this time, although the rotation of the drive wheels 14 is transmitted to the counter gear 54 via the differential device 38, the reduction gear mechanism 34, the output gear 56, and the like, the rotation of the counter gear 54 is cut off by the two-way clutch TWC being set to the one-way mode, and the rotation is not transmitted to the gear mechanism 28 side. Therefore, even when the vehicle speed V is high, since the rotation is not transmitted to the gear mechanism 28 side, the high rotation of the gear mechanism 28 and the first clutch C1 (specifically, a drum or the like constituting the first clutch C1 coupled to the two-way clutch TWC) during high vehicle speed running is suppressed.

In addition, although the vehicle is in the driven state in which the vehicle is driven by the inertia of the vehicle 10 during the inertia running, when the operating position POSsh is switched to the M1 position, the two-way clutch TWC is switched to the lock-up mode, and therefore, the engine brake is generated. When the driver switches the operation position POSsh to the D position in such a traveling state, the two-way clutch TWC is switched from the lockup mode to the one-way mode, but even if the TWC hydraulic pressure Ptwc of the hydraulic actuator 41 that switches the mode of the two-way clutch TWC is controlled to be zero, the one end of the second support plate 72b of the two-way clutch TWC and the second wall surface 80b of the second output side rotation member 70b are in a mutually forced state (see fig. 3), and therefore, the contact between the second support plate 72b and the second wall surface 80b is not released, and there is a possibility of an unlocking failure in which the two-way clutch TWC is not switched to the one-way mode. Further, in the case where the vehicle continues to travel in a state where the two-way clutch TWC is not switched to the one-way mode (i.e., the lock-up mode), and the vehicle speed V is increased, and the state where the lock-up mode is maintained after the shift-up to the belt travel mode is performed, the rotation of the drive wheels 14 is transmitted to the first clutch C1 via the two-way clutch TWC, so that the first clutch C1 (specifically, a drum or the like constituting the first clutch C1 coupled to the two-way clutch TWC) may be rotated at a high rotation.

In order to solve the above problem, the electronic control device 100 has a function of increasing the engine torque Te of the engine 12 when a request for switching the two-way clutch TWC to the one-way mode is satisfied while the two-way clutch TWC is in the locked mode and the forward travel is performed in the driven state. Hereinafter, control when a request for switching the two-way clutch TWC to the one-way mode is satisfied while the two-way clutch TWC is in the locked mode and traveling in the driven state will be described.

In order to execute the above control, the shift control unit 122 functionally includes a switching request determination unit 126 functioning as a switching request determination means and an unlocking failure determination unit 128 functioning as an unlocking failure determination means. The engine control unit 120 and the gear shift control unit 122 correspond to the control unit of the present invention.

The switching request determination unit 126 determines whether or not a request to switch the operation position POSsh from the M1 position to the D position is satisfied in the driven state in which the vehicle 10 travels by inertia. The request for switching from the M1 position to the D position is determined to be satisfied when the switching operation (manual operation) from the M1 position to the D position of the operation position POSsh by the driver is completed. When the vehicle speed V is equal to or higher than a predetermined vehicle speed V1 set in advance and the accelerator operation amount θ acc of the accelerator pedal is equal to or lower than a predetermined value θ 1, the switching request determining unit 126 determines that the vehicle 10 is in the driven state. The predetermined vehicle speed V1 and the predetermined value θ 1 of the accelerator operation amount θ acc are experimentally or designably obtained in advance, and are set as threshold values of a travel range in which the vehicle 10 is in a driven state.

When the switching request determining portion 126 determines that the operating position POSsh is switched from the M1 position to the D position in the driven state, the shift control portion 122 starts switching the two-way clutch TWC to the one-way mode. Specifically, the shift control portion 122 controls the TWC hydraulic pressure Ptwc (instruction pressure) of the hydraulic actuator 41 that controls the switching of the mode of the two-way clutch TWC to zero. Thereby, the TWC hydraulic pressure Ptwc (actual pressure) decreases so as to follow the instruction pressure.

The unlock failure determination section 128 determines whether or not an unlock failure occurs in which the two-way clutch TWC is not switched from the lock-up mode to the one-way mode after a predetermined time TK has elapsed from when the two-way clutch TWC starts to be switched to the one-way mode, the predetermined time TK being set to a time required for the two-way clutch TWC to be switched to the one-way mode in a state where the two-way clutch TWC is not in a mutually forced state, that is, in a driving state of the vehicle 10, between the second support plate 72b and the second wall surface 80b, the unlock failure determination section 128 calculates a rotation speed difference Δ Ntwc (| Ntwcin — Ntwcout |) between an input rotation speed Ntwcin of the input side rotating member 68 of the two-way clutch TWC and an output rotation speed ntcout of the output side rotating member 70, determines whether or not the rotation speed difference Δ Ntwc is a predetermined determination threshold value α or less (Δ Ntwc ≦ α), the determination threshold value α is obtained experimentally or contrivedly, and is set to be a rotation speed difference corresponding to the two-way clutch TWC, and the two-way clutch TWC is set to a rotation speed difference determination threshold value α, in other words, the two-way clutch TWC is set to be output in a two-way clutch TWC state.

When it is determined by the unlock failure determination section 128 that an unlock failure has occurred, the engine control section 120 outputs a command to the engine control device 42 to raise the engine torque Te by a predetermined value β for a predetermined time T that has been set in advance, the predetermined value β that is a target value for the increase in the engine torque Te is experimentally or contrived in advance and is set to a value that is extremely small in a range in which the torque acting in the vehicle forward direction that is transmitted to the two-way clutch TWC increases and in which the driver does not feel a change in the driving force due to the torque, and the predetermined time T is experimentally or contrived and is set to a time at which the two-way clutch TWC can be switched to the one-way mode by transmitting the torque in the vehicle forward direction to the two-way clutch TWC, because the torque applied in the vehicle forward direction is transmitted to the two-way clutch TWC, when the torque is transmitted to the two-way clutch TWC, the input side spring 80b of the two-way clutch TWC shown in fig. 3 is not rotated, and the input side of the input side spring 68 is moved to the input side of the second rotating member 68, and the input side of the two-way clutch TWC, the input side spring 70, the input side of the input side, and the input side of the input member.

Fig. 5 is a flowchart illustrating a main part of the control operation of the electronic control device 100, that is, the control operation when the two-way clutch TWC is switched to the one-way mode while the two-way clutch TWC is in the locked mode and is traveling in the driven state. This flowchart is repeatedly executed during forward running of the vehicle.

First, in step ST1 (hereinafter, the "step" is omitted) corresponding to the control function of the switching request determining section 126, it is determined whether or not the request for switching the operation position POSsh from the M1 position to the D position is satisfied during traveling in the driven state, in ST1, if negative, the present routine is ended, in ST1, if positive, switching of the two-way clutch TWC to the one-way mode is started in ST2 corresponding to the control function of the shift control section 122, next, in ST3 corresponding to the control function of the unlocking failure determining section 128, an unlocking failure in which the two-way clutch TWC is not switched to the one-way mode is determined based on whether or not the rotation speed difference Δ Ntwc (| Ntwcin-Ntwcout |) is equal to or less than the determination threshold α, in ST 3528, the present routine is ended, in ST2, in case ST3, the present routine is unlocked, in case where the unlocking failure occurs, the predetermined value is applied between the engine wall surface control function and the engine support plate 120, and the engine support plate 80, the second engine support plate 80 is moved forward, and the engine torque is applied to the engine support plate 72b, the second engine is increased, the engine control function is performed in the two-direction indicated by the two-TWC control function.

Fig. 6 is a timing chart showing a control result based on the control operation of the electronic control device 100. Specifically, a time chart showing the control result when the operating position POSsh is switched from the M1 position to the D position during the running with the two-way clutch TWC in the locked mode and the vehicle 10 in the driven state is shown.

In fig. 6, the vertical axis shows, in order from above, the rotation speed difference Δ Ntwc, the SL1 hydraulic pressure Psl1 (instruction pressure) for controlling the first clutch C1, the SL2 hydraulic pressure Psl2 (instruction pressure) for controlling the second clutch C2, the TWC hydraulic pressure Ptwc (instruction pressure) supplied to the hydraulic actuator 41 for controlling the switching of the two-way clutch TWC, the engine torque Te, the TWC state, and the TWC unlock failure determination. In addition, "LOCK" indicates a case where the two-way clutch TWC is switched to the LOCK-up mode, and "UNLOCK" indicates a case where the two-way clutch TWC is switched to the one-way mode in the TWC state. In the TWC unlock failure determination, "OFF" indicates that it is determined that the two-way clutch TWC unlock failure has not occurred, and "ON" indicates that it is determined that the two-way clutch TWC unlock failure has occurred.

At the time point of T1 shown in fig. 6, by switching the operating position POSsh from the position M1 to the position D during the driven travel, the requirement for switching the two-way clutch TWC from the lockup mode to the one-way mode is established, the TWC hydraulic pressure Ptwc (indicated pressure) is controlled to zero, following this, the actual pressure of the TWC hydraulic pressure Ptwc will decrease, at the time point of T2 when the predetermined time TK has elapsed from the time point of T1, when the rotational speed difference Δ Ntwc becomes equal to or less than the determination threshold α, it is determined that the two-way clutch TWC is in the lockup mode ("LOCK"), and it is determined that an unlocking failure of the two-way clutch TWC has occurred, in association with this, at the time point of T2, the engine torque Te of the engine 12 starts to increase, at the time point of T2 to T4, the engine torque Te is controlled to a predetermined value β, by controlling the engine torque Te to a predetermined value β, so that the torque acting in the vehicle forward direction is applied to the two-way clutch TWC, reaches the two-way clutch TWC, and the rotational speed difference reaches the one-way clutch TWC start time point, after the one-way clutch is switched to be gradually increased ("TWC OFF time point of T-way clutch TWC". 6853, the rotational speed difference "TWC is determined to be equal to the time point of T465, and the two-way clutch TWC, the two-way clutch TWC start time point of the two-way clutch TWC, the two-way clutch TWC is increased.

As described above, according to the present embodiment, in the case where the request for switching the two-way clutch TWC to the one-way mode is satisfied during the forward travel with the two-way clutch TWC in the locked mode and the vehicle 10 in the driven state, the engine torque Te of the engine 12 is increased to transmit the torque acting on the drive side to the two-way clutch TWC, and the two-way clutch TWC is switched to the one-way mode. Therefore, since the one-way mode is switched by the two-way clutch TWC and the rotation is not transmitted to the first clutch C1, the high rotation of the first clutch C1 can be suppressed.

Further, according to the present embodiment, when the rotation speed difference Δ Ntwc is equal to or less than the determination threshold α, the engine torque Te of the engine 12 increases, and therefore, although the two-way clutch TWC is switched to the one-way mode, a shock and deterioration of fuel efficiency due to the increase of the engine torque Te of the engine 12 are avoided.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the present invention is also applicable to other embodiments.

For example, although in the foregoing embodiment, the two-way clutch TWC is configured to transmit power acting in the vehicle forward direction in the one-way mode and to transmit power in the vehicle forward direction and the vehicle reverse direction in the lock-up mode, the two-way clutch of the invention is not necessarily limited thereto. For example, the two-way clutch may be configured to be switchable to a one-way mode and a lock-up mode, and also to a free mode in which power transmission in both the forward direction and the reverse direction of the vehicle is interrupted, a mode in which only power in the reverse direction of the vehicle is transmitted, or the like.

Further, in the foregoing embodiments, the structure of the two-way clutch TWC is not necessarily limited to the present embodiment. For example, the two-way clutch may be constituted by a first one-way clutch and a second one-way clutch which are separately provided, the first one-way clutch may be constituted so as to be able to transmit power in the forward direction of the vehicle, the second one-way clutch may be constituted so as to be able to transmit power in the reverse direction of the vehicle, and the second one-way clutch may be constituted so as to be able to switch to a mode in which power transmission in both the forward direction of the vehicle and the reverse direction of the vehicle is cut off. The first one-way clutch may be configured to be switchable to a mode in which power transmission in both the vehicle forward direction and the vehicle reverse direction is cut off. The main point is that this configuration can be changed as appropriate as long as it is a two-way clutch that can be switched to at least a one-way mode and a lock-up mode.

The above-described embodiment is merely one embodiment, and the present invention can be implemented in various modifications and improvements based on the knowledge of those skilled in the art.

Description of the symbols

12: an engine;

14: a drive wheel;

16: a power transmission device for a vehicle;

68: an input-side rotating member (front and rear rotating members);

70a, 70 b: first and second output-side rotating members (front and rear rotating members);

100: an electronic control device (control device);

120: an engine control unit (control unit);

122: a shift control unit (control unit);

PT: a power transmission path;

PT 1: a first power transmission path;

PT 2: a second power transmission path;

c1: a first clutch;

c2: a second clutch;

TWC: a bidirectional clutch (sub clutch).

Claims

1. A control device (100) for a vehicle power transmission device (16), wherein two power transmission paths, namely a first power transmission path (PT1) and a second power transmission path (PT2), are provided in parallel between an engine (12) and drive wheels (14), the first power transmission path (PT1) is provided with a first clutch (C1) and a secondary clutch (TWC), the second power transmission path (PT2) is provided with a continuously variable transmission (24) and a second clutch (C2), the first clutch (C1) is engaged and the second clutch (C2) is released, so that the first power transmission path (PT1) is allowed to transmit power, the first clutch (C1) is released and the second clutch (C2) is engaged, thereby enabling the second power transmission path (PT2) to perform power transmission,

the control device (100) for the vehicle power transmission device (16) is characterized in that,

the sub-clutch (TWC) is configured by a two-way clutch (TWC) that can be switched between at least two modes, a one-way mode in which power is transmitted in a driving state of the vehicle (10) and power is cut off in a driven state of the vehicle (10), and a lock-up mode in which power is transmitted in the driving state and the driven state of the vehicle (10),

the control device (100) of the vehicle power transmission device (16) is provided with control units (120, 122), and when a request for switching the two-way clutch (TWC) to the one-way mode is satisfied while the two-way clutch (TWC) is in the locked mode and is in the driven state and traveling forward, the control units (120, 122) increase the engine torque of the engine.

2. The control device (100) of a power transmission device (16) for a vehicle according to claim 1,

the control units (120, 122) increase the engine torque (Te) of the engine (12) when the difference (DeltaNtwc) in the rotational speeds of the rotary members (68, 70) before and after the two-way clutch (TWC) is equal to or less than a preset determination threshold (α).

3. The control device (100) of a vehicular power transmitting apparatus (16) according to claim 1 or 2,

the control units (120, 122) increase the engine torque (Te) so that the torque in the forward direction of the vehicle, which is transmitted from the engine (12) to the two-way clutch (TWC), is temporarily increased.